WO2012002279A1 - 負荷感応型変速装置 - Google Patents
負荷感応型変速装置 Download PDFInfo
- Publication number
- WO2012002279A1 WO2012002279A1 PCT/JP2011/064561 JP2011064561W WO2012002279A1 WO 2012002279 A1 WO2012002279 A1 WO 2012002279A1 JP 2011064561 W JP2011064561 W JP 2011064561W WO 2012002279 A1 WO2012002279 A1 WO 2012002279A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- ring
- load
- gear
- carrier
- contact
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by orbital gears
- F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
- F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
- F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
- F16H61/0293—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being purely mechanical
- F16H61/0295—Automatic gear shift control, e.g. initiating shift by centrifugal forces
Definitions
- the present invention relates to a load-sensitive transmission, and more particularly to a transmission in which a shift is performed by a mechanical operation in accordance with a change in a load acting on an output system.
- Patent Document 1 discloses a chain block that transmits an operating force to a hand wheel to a load sheave.
- the hand wheel is operated to be wound up with no load.
- Patent Document 1 when performing a hoisting operation with no load, by moving the transmission plate, the clutch plate, and the like along the axial direction of the drive shaft by the rotational force of the handwheel, The rotational force of the handwheel is transmitted to the planetary gear carrier (gear holding plate in the literature) (function of the first clutch means).
- the ring gear (fixed gear in the literature) of the planetary gear is fixed, and the sun gear (output shaft in the literature) is splined to the drive shaft, so the rotational force of the carrier is transmitted to the drive shaft in an accelerated state. Rotate the load sheave at high speed.
- the transmission plate, clutch plate, etc. Is moved in the reverse direction (the reverse direction compared to no load), the transmission to the planetary gear is cut off, and the rotational force of the handwheel is transmitted to the drive shaft by the pressure contact of the brake plate (second clutch means) Function), and as a result, the load sheave rotates at a low speed.
- Patent Document 1 has an effective aspect in which a shift operation is automatically performed in response to a change in load without including sensors and actuators for realizing electrical control. Is.
- Patent Document 1 when two types of clutch means are used and a planetary gear mechanism is used only at the time of speed increase, the number of parts is large and the transmission system is likely to be complicated and there is room for improvement.
- An object of the present invention is to configure a transmission that automatically shifts in response to a load with a small number of parts.
- a feature of the present invention is a planetary gear including a sun gear, a ring gear surrounding the sun gear, a planetary gear meshing with the sun gear and the ring gear, a carrier capable of revolving with the planetary gear, and an output system for extracting the revolving motion of the carrier.
- Load acquisition means for taking out the magnitude of the load acting on the output system as a mechanical operation amount is provided, and when the load acquired by the load acquisition means is less than a set value, the sun gear, the ring gear, and the When the planetary gear and the carrier are integrally rotated, and the load acquired by the load acquisition means exceeds the set value, the carrier prevents the rotation of the sun gear and the ring gear other than the input of the driving force. Is provided with a switching means for allowing the rotation.
- the switching means integrally rotates the sun gear, the ring gear, the planetary gear, and the carrier to realize a high-speed transmission state.
- the switching means allows the rotation of the carrier while preventing the rotation of the sun gear and the ring gear other than the input of the driving force. Realize the state. That is, as shown in Patent Document 1, there are two types of transmission systems, a transmission system that realizes a high-speed transmission state and a transmission system that realizes a low-speed transmission state, and 2 for selecting these two types of transmission systems.
- the transmission system of the present invention is simplified as compared with the one having a kind of clutch means.
- the switching means when switching between the high-speed transmission state and the low-speed transmission state, controls some functions of the components of the planetary gear transmission mechanism, so that the high-speed transmission state and the low-speed transmission state are controlled.
- the driving force is transmitted to the output system via the planetary gear transmission system, thereby suppressing an increase in the size of the transmission system.
- the planetary gear mechanism two types of transmission modes for realizing deceleration can be considered. One of them is to output the driving force input to the sun gear from the carrier while the ring gear is fixed. The other is to output the driving force input to the ring gear from the carrier while the sun gear is fixed. For this reason, the decelerating state is realized by preventing rotation of the sun gear and the ring gear other than those that receive the driving force.
- a transmission that automatically shifts in response to a load can be configured with a small number of parts.
- the present invention includes an input shaft that transmits a driving force to the sun gear as an input system, and an output shaft that is connected to the carrier as the output system.
- the load acquisition means is an operation ring that is rotatably supported by a coaxial core and a coaxial core of the ring gear; a biasing member that biases the relative rotation posture of the operation ring and the ring gear to a neutral posture; and
- the load acquisition means includes an operating ring, an urging member, and an operating body.
- the urging force of the urging member acts to operate.
- the relative rotational posture of the ring and the ring gear is maintained in a neutral posture, and the operating body is in a high-speed transmission posture.
- the relative rotational attitude of the operating ring and the ring gear deviates from the neutral attitude against the urging force of the urging member, and the operating body Reaches a low-speed transmission posture.
- the switching means includes the operating body, an engaging portion that engages with the operating body when the operating body is in the high-speed transmission posture, and is integrated with the carrier.
- a lock portion that abuts against the operating body and prevents the ring gear from rotating when in a low-speed transmission posture may be provided.
- the switching means includes the operating body, the engaging portion, and the lock portion, so that when the operating body is in the high-speed transmission posture, it engages with the engaging portion of the carrier.
- a high-speed transmission state in which the transmission system from the sun gear to the output shaft is integrally rotated is realized.
- the operating body when the operating body is in the low-speed transmission posture, it can be detached from the engaging portion of the carrier and newly brought into contact with the locking portion of the fixed system.
- the carrier can be rotated in a state in which the rotation of the ring gear is prevented, and a low-speed transmission state decelerated by the planetary gear transmission system is realized.
- the operating body is supported by the ring gear so as to be swingable about a pivot shaft that is parallel to the input shaft and the output shaft, and is engaged with the engaging portion.
- the plurality of engaging portions are formed in a gear shape centered on the axis of the carrier,
- the plurality of lock portions may be formed in an external gear shape or an internal gear shape centering on an axis of the carrier with respect to an inner surface of a gear case as a fixed system.
- the engaging pieces of the operating body in the high-speed transmission posture are a plurality of engaging portions formed in an external gear shape on the carrier. It is possible to engage with either of these.
- the contact piece of the operating body having a low-speed transmission posture can be brought into contact with a plurality of lock portions formed in the fixed system. It becomes.
- an arc-shaped long hole centered on the input shaft is formed so that the pivot shaft penetrates the operating ring, and the input shaft is formed with respect to the long hole formed in the operating body.
- a linkage shaft that is in a parallel posture with the penetrating shaft may pass therethrough, and the linkage shaft may be coupled to the operating ring.
- the operating body is elastically deformed in a state where the contact piece receives the reaction force from the lock portion when the contact piece contacts the lock portion, and the contact piece rides on the gear-shaped portion.
- You may comprise.
- the working body when switching from high speed to low speed, the contact state between the engaging piece and the engaging portion of the working body, and the contact piece of the working body and the lock
- the respective forces in the contact state with the part may antagonize, resulting in a so-called “fixed state”, and switching for shifting may not be performed well.
- the operating body can be elastically deformed in a state where the contact piece rides on the gear-like portion by receiving a reaction force from the lock portion when the contact piece comes into contact with the lock portion. If configured, the operating body is locked even if the respective forces of the contact state between the engagement piece and the engagement portion and the contact state between the contact piece and the lock portion antagonize.
- the contact piece is elastically deformed and retracted in a state where the contact piece rides on the gear-like part under the reaction force from the part.
- the engagement piece of the operating body is allowed to rotate in a direction away from the engagement portion within a range in which the contact piece is retracted.
- the operating body that has been in contact with the engaging portion comes out of the engaging portion, and the operating body thereafter meshes with the lock portion.
- the operating body is in a fixed state between the engaging portion and the lock portion.
- the operating body includes a main body portion and a deforming portion connected to the main body portion and the abutting piece, and when the abutting piece abuts on the lock portion, a reaction from the lock portion occurs.
- the deforming portion may be configured to be elastically deformable in a state where the contact piece rides on the gear-shaped portion under force.
- the operating body includes a main body portion and a deforming portion connected to the main body portion and the contact piece, and when the contact piece comes into contact with the lock portion, a reaction force from the lock portion is generated.
- the deforming portion is configured to be elastically deformable in a state where the abutting piece rides on the gear-shaped portion
- the actuating body is configured such that the abutting piece that receives the reaction force from the lock portion is the gear-shaped portion.
- the deformed portion is elastically deformed and retreats in the state where it rides on.
- the engagement piece of the operating body is allowed to rotate in a direction away from the engagement portion within a range in which the contact piece is retracted.
- the operating body that has been in contact with the engaging portion comes out of the engaging portion, and the operating body thereafter meshes with the lock portion.
- the operating body is in a fixed state between the engaging portion and the lock portion.
- the contact piece since the contact piece is provided apart from the main body, the contact piece that has received the reaction force from the lock part can move backward without being obstructed by the main body, The rotation of the engagement piece in the direction away from the engagement portion is allowed more smoothly.
- the operating body only needs to include a deforming portion that is elastically deformed at a part thereof (deforms when receiving a load and returns to the original shape when the load is not received). Therefore, the manufacturing cost of the operating body can be reduced, and the strength of the operating body itself can be maintained by increasing the rigidity of the portion other than the deformed portion.
- the operating body is extended from the vicinity of the pivot shaft toward both ends so that the deformed portion on the outer peripheral side is partly separated from the main body portion on the inner peripheral side,
- the deforming portion may be connected to the main body portion and the abutting piece by providing the abutting piece at the end of the main body.
- the deforming portion is positioned on the outer peripheral portion of the main body portion, the length of the deforming portion can be sufficiently secured, so that the deforming portion can be easily elastically deformed.
- the contact piece is formed in an L shape covering the main body portion in a state of being separated from the end portion of the main body portion, and an end edge portion serving as an end portion of the operating body; And an inner edge portion extending from the edge portion toward the main body portion, and a convex contact portion capable of contacting the end edge portion may be formed at an end portion of the main body portion.
- the abutment piece includes an end edge portion that is an end portion of the operating body, and an inner edge portion that extends from the end edge portion toward the end portion of the main body portion, and is separated from the end portion of the main body portion. Since the abutting piece is formed in an L shape covering the portion, the reaction force from the lock portion and the low-speed transmission in a state where the abutment piece abuts both the engagement portion and the lock portion by the end edge portion and the inner edge portion. Both reaction forces from the lock portion in the state can be accepted. Also, by providing a convex contact portion at the end of the main body, the deformable portion is allowed to be elastically deformed until the contact piece contacts the contact portion, and the contact piece is a convex contact. It does not elastically deform after contacting the part. As a result, excessive deformation of the deforming portion can be easily prevented, and the durability of the operating body can be improved.
- the present invention includes an input shaft that transmits a driving force to the sun gear as an input system, and an output shaft on a coaxial core and a coaxial core that the carrier revolves as the output system, A cam ring formed on a surface of the cam ring and the carrier facing each other; and a cam ring that is capable of transmitting torque to the output shaft and movable along the axis of the output shaft; And a biasing member that biases the cam ring in the direction of the carrier, and when the load acting on the output shaft is less than a set value, the cam ring is at a reference position, and the output shaft When the load acting on the vehicle exceeds the set value, the cam ring is configured to reach a shift position away from the carrier,
- the switching means includes a shift ring that is in a high-speed transmission position when the cam ring is in a reference position and is in a low-speed transmission position when the cam ring is in a shift position while maintaining a contact state with the ring gear.
- the shift ring includes a first contact portion that rotates the ring gear and the carrier integrally by contacting the carrier when in the high-speed transmission position, and is fixed when the shift ring is in the low-speed transmission position. You may provide the 2nd contact part which prevents rotation of a ring gear by contacting.
- a third contact portion provided at an outer end of the shift ring comes into contact with the ring gear to be integrated, and the first contact portion of the shift ring is A high-speed transmission state in which the planetary gear transmission system is rotated integrally with the carrier to rotate the input shaft and the output shaft at the same rotational speed may be realized.
- the third contact portion provided at the outer end of the shift ring maintains the state of contacting the ring gear, and the One contact portion is separated from the carrier, and the second contact portion of the shift ring newly contacts the transmission case to lock the rotation of the ring gear, thereby realizing a low-speed transmission state in which the rotation of the carrier is allowed. May be.
- FIG. 3 is a sectional view taken along line III-III in FIG.
- FIG. 4 is a sectional view taken along line IV-IV in FIG. 1.
- FIG. 5 is a cross-sectional view taken along line VV in FIG.
- FIG. 6 is a sectional view taken along line VI-VI in FIG.
- the load-sensitive transmission of the present invention includes an input shaft 1 as an input system and an output shaft 2 as an output system in a mission case M.
- a planetary gear transmission mechanism P (an example of a planetary gear transmission system) is provided inside the mission case M.
- a high-speed transmission that has a speed equal to the rotational speed of the input shaft 1 as shown in FIG. 1, FIG. 3, and FIG.
- the output shaft 2 is driven in the state.
- the planetary gear transmission mechanism P decelerates and the speed is lower than the rotational speed of the input shaft 1.
- the output shaft 2 is driven in the transmission state.
- This load-sensitive transmission has a light load in the middle of the operating range, such as a sliding door of an automobile, and is provided in a drive source or the like that is driven when the load increases. Since the ratio is changed, the increase in size of the electric motor is suppressed.
- a drive system that adjusts the angle of the seat back and a drive system that opens and closes the door glass can be used in all automobiles, but it can be applied to other than automobiles.
- the planetary gear speed change mechanism P includes a sun gear 11 connected to the input shaft 1, a ring gear 12 disposed at a position surrounding the sun gear 11, three planetary gears 13 meshing with the sun gear 11 and the ring gear 12, and a plurality of planetary gears 13. And a carrier 14 capable of revolving.
- the carrier 14 is connected to the output shaft 2 for taking out the revolving motion, and includes three idler shafts 15 for freely supporting the three planetary gears 13.
- the carrier is connected to the ends of the three idler shafts 15.
- a ring 14A is provided.
- the input shaft 1 and the output shaft 2 are disposed on the coaxial core X and the coaxial core. Accordingly, the axis of the sun gear 11, the axis of the ring gear 12 (the axis of the center of the ring), and the revolution axis of the carrier 14 are arranged coaxially with the main axis X.
- This load-sensitive transmission device includes load acquisition means A and switching means B.
- the load acquisition means A takes out the magnitude of the load acting on the output shaft 2 (output system) as a mechanical operation amount.
- the switching unit B realizes a high-speed transmission state in which the sun gear 11, the ring gear 12, the planetary gear 13, and the carrier 14 are rotated together. Further, when the load acquired by the load acquisition unit A exceeds the set value, the switching unit B realizes a low-speed transmission state that allows the rotation of the carrier 14 while preventing the ring gear 12 from rotating.
- An operating ring 16 is provided that is externally fitted to the ring gear 12 so as to be rotatable about the main axis X, and a plurality of urging members that maintain the operating ring 16 and the ring gear 12 in a predetermined relative rotational attitude about the main axis X.
- the coil spring 17 is provided.
- the load acquisition means A is configured to include the operating ring 16, the plurality of coil springs 17, and the operating body 21.
- the actuating body 21 is linked to the carrier 14 and the ring gear 12 so that the posture changes in linkage with the load acting on the carrier 14. Details of this linkage will be described later.
- a spring accommodating space 16A is formed in a groove shape on the outer periphery of the operating ring 16, a pair of spring locking portions 16B is formed in the spring accommodating space 16A, and a pair of insertion ports 16C are formed on the inner periphery of the operating ring 16.
- a pair of projecting pieces 12A that are inserted through the insertion port 16C are projected outward.
- the operating ring 16 and the ring gear 12 are maintained in the neutral posture shown in FIG. 4 with the main shaft core X as the center by providing the coil spring 17 over the protruding piece 12A inserted through the insertion port 16C and the spring locking portion 16B.
- the urging force to act acts from the coil spring 17.
- An engagement plate 20 having a shape surrounding the output shaft 2 is fixed on the surface of the carrier 14, and a plurality of engagement portions C are formed on the outer peripheral portion of the engagement plate 20 as external gears with the main shaft core X as the center. Is formed.
- a block portion 4 having a shape surrounding the output shaft 2 is formed on the inner surface of the transmission case M as a fixed system, and a plurality of lock portions D are formed in an external gear shape with the main shaft core X as the center on the outer periphery of the block portion 4. Is formed.
- a ring portion 5 is formed along the operation ring 16 on the inner surface of the transmission case M, and a plurality of lock portions D are formed in an inner gear shape around the main shaft core X on the inner periphery of the ring portion 5. Yes.
- the three actuating bodies 21 described above are provided so as to selectively switch to a state of contacting the lock portion D.
- the load acquisition means A is configured to include an operating ring 16, a coil spring 17, and an operating body 21.
- the actuating body 21 is supported by the ring gear 12 so as to be swingable by a pivot shaft 22 in a posture parallel to the main axis X.
- the operating ring 16 is formed with an arc-shaped long hole 16S centering on the main shaft core X so that the pivot shaft 22 penetrates.
- a linkage shaft 23 that is parallel to the main axis X passes through a long hole 21 ⁇ / b> S formed in the actuation body 21, and the linkage shaft 23 is connected to the actuation ring 16.
- a screw portion is formed at the end of the pivot shaft 22, and the pivot shaft 22 is supported by the ring gear 12 by screwing the screw portion into a screw hole of the ring gear 12.
- a threaded portion is formed at the end of the linkage shaft 23, and the linkage shaft 23 is connected to the actuation ring 16 by screwing this threaded portion into the screw hole of the actuation ring 16.
- the operating body 21 is formed of a plate-like material, and includes an engagement pin 24 (an example of an engagement piece) that engages with the engagement portion C described above, and an external tooth-like lock portion D described above.
- a pair of inner contact pieces 21 ⁇ / b> A that come into contact with each other and a pair of outer contact pieces 21 ⁇ / b> B that come into contact with the above-described internal tooth-shaped lock portion D are formed.
- the switching means B is provided on the operating body 21, the engagement portion C formed on the engagement plate 20, the lock portion D formed on the block portion 4, and the ring portion 5.
- the lock part D is formed. That is, the operating body 21 is included in both the load acquisition means A and the switching means B, and the use of the operating body 21 in this way reduces the number of parts.
- the lock part D may be formed on either the block part 4 or the ring part 5.
- the lock portion D is formed only on one side as described above, only one of the inner contact piece 21A and the outer contact piece 21B of the operating body 21 needs to be formed.
- the engagement pin 24 of the operating body 21 is engaged with any one of the plurality of engagement portions C formed on the outer periphery of the engagement plate 20.
- the ring gear 12 and the carrier 14 are integrated, and as a result, a high-speed transmission state in which the sun gear 11, the ring gear 12, the planetary gear 13, and the carrier 14 are integrally rotated is realized.
- the engaging pin 24 of the operating body 21 is separated from the engaging portion C of the engaging plate 20.
- the inner contact piece 21A of the operating body 21 newly contacts the lock portion D of the block part 4, and the outer contact piece 21B of the operation body 21 newly contacts the lock part D of the ring part 5.
- the ring gear 12 is locked to the transmission case M, the rotation of the ring gear 12 is prevented, and a low-speed transmission state that allows the rotation of the carrier 14 is realized.
- the internal contact of the operating body 21 is immediately before the engaging pin 24 of the operating body 21 is completely separated from the engaging portion C of the engaging plate 20.
- the operation timing is set so that the contact piece 21 ⁇ / b> A contacts the lock part D of the block part 4 and the outer contact piece 21 ⁇ / b> B of the operating body 21 contacts the lock part D of the ring part 5.
- the posture of the operating body 21 is switched by setting the operation timing as described above, the inner abutment piece 21A is separated while the engaging pin 24 is separated from the engaging portion C in a series of flows in which the posture is switched. Then, the outer contact piece 21B comes into contact with the lock portion D.
- the operation timing is set so that the engagement pin 24 of the operating body 21 starts engagement with the plurality of engagement portions C on the outer periphery of the engagement plate 20.
- the load sensitive transmission acquires the load acting on the output shaft 2 as a mechanical operation amount by the load acquisition means A.
- the switching means B connects the ring gear 12 and the carrier 14 to create a state in which the planetary gear speed change mechanism P is rotated integrally, thereby realizing a high-speed transmission state.
- the switching means B allows the rotation of the carrier 14 while preventing the rotation of the ring gear 12, so that the planetary gear transmission mechanism P is decelerated to realize a low-speed transmission state.
- the load-sensitive transmission of the present invention acquires the load acting on the output shaft 2 as a mechanical operation amount without providing a sensor or actuator for performing electrical control, and switches by this operation. Switching between the high speed transmission state and the low speed transmission state is realized by the switching operation of the means.
- the operating body 21 is included in both the load acquisition means A and the switching means B, and a reduction in the number of parts is realized as compared with a structure including a plurality of clutches.
- the transmission system is configured such that power is transmitted to the planetary gear transmission mechanism P in either the high-speed transmission state or the low-speed transmission state, for example, the transmission system includes a plurality of transmission systems. The transmission system is downsized compared to the one equipped with a clutch for selecting the system.
- the load-sensitive transmission of the present invention may be configured as follows in addition to the above-described embodiment (in this another embodiment, the same number as that of the above-described embodiment is used for the component having the same function as the above-described embodiment). ).
- the contact piece 21A of the operating body 21 is immediately before the operating body 21 is completely separated from the engaging portion C of the engaging plate 20 in order to surely switch the posture of the operating body 21.
- the operation timing is set so as to contact the lock portion D of the block portion 4.
- the entire actuating body 21 is composed of a rigid body, the respective forces of the contact state between the actuating body 21 and the engaging portion C and the contact state between the actuating body 21 and the lock portion D are antagonistic. As a result, there is a possibility that the so-called “fixed state” may not be successfully switched for shifting.
- the actuating member 21 when the abutment piece 21A abuts against the lock portion D, the actuating member 21 receives a reaction force from the lock portion and the abutment piece 21A is in the gear shape of the lock portion D. It is configured to be elastically deformable while riding on the part.
- the operating body 21 is formed of a plate-like material, and the engagement convex portion 24 (an example of an engagement piece) that engages with the engagement portion C is described above.
- a pair of abutting pieces 21 ⁇ / b> A that abut against the externally toothed locking portion D is formed.
- the actuating body 21 extends from the vicinity of the pivot shaft 22 toward both ends in such a manner that the outer peripheral deformed portion 21C is partly separated from the inner peripheral main body portion 21D, and at the end of the deformable portion 21C.
- a contact piece 21A is provided. That is, the deformation portion 21C is connected to the main body portion 21D and the contact piece 21A.
- 21 A of contact pieces are formed in the L-shape which covers main-body part 21D in the state spaced apart from the edge part of main-body part 21D, from edge part 21Aa used as the edge part of the action body 21, and edge part 21Aa And an inner edge portion 21Ab extending toward the main body portion 21D.
- a convex contact portion 21E that can contact the end edge portion 21Aa of the contact piece 21A is formed at the end portion of the main body portion 21D.
- the deformation portion 21C is made of spring steel or the like and is configured to be elastically deformable.
- the contact piece 21A receives a reaction force from the lock part D and moves backward while riding on the gear-shaped part of the lock part D, the deformed part 21C is elastic until the contact piece 21A comes into contact with the contact part 21E.
- the contact piece 21A continues to be deformed and no longer receives the reaction force from the lock portion D, it returns to its original shape.
- the engagement convex portion 24 of the operating body 21 is engaged with any of the plurality of engagement portions C formed on the outer periphery of the engagement plate 20.
- the ring gear 12 and the carrier 14 are integrated, and as a result, a high-speed transmission state in which the sun gear 11, the ring gear 12, the planetary gear 13, and the carrier 14 are integrally rotated is realized.
- the deforming portion 21C continues to be elastically deformed until it retracts in the direction of the arrow and the abutting piece 21A comes into contact with the contact portion 21E. Since the abutting piece 21A is provided at the end of the deforming portion 21C so as to be separated from the main body portion 21D, the operating body 21 has a main body portion when the abutting piece 21A receives a reaction force from the lock portion D. The contact piece 21A can be moved backward without being obstructed by 21D.
- the main body 21D of the operating body 21 is allowed to rotate in a direction in which the engaging convex portion 24 is disengaged from the engaging portion C by the amount of the abutting piece 21A being retracted.
- the engaging convex portion 24 of the operating body 21 is first disengaged from the engaging portion C, and the power transmission from the engaging plate 20 to the operating ring 16 is cut off.
- the contact piece 21A is completely engaged with the lock portion D while the elastic deformation of 21C is returned to the original state.
- the actuating body 21 receives the reaction force of the lock part D at the end edge part 21Aa of the contact piece 21A and continues to the contact piece 21A.
- the deformation portion 21C is configured to be elastically deformed.
- the actuating body 21 maintains the meshing state between the abutting piece 21A and the lock portion D by the inner edge 21Ab of the abutting piece 21A coming into contact with the end of the main body 21C. 21 low-speed transmission posture is set stably.
- the abutting piece 21A includes the end edge portion 21Aa and the inner edge portion 21Ab extending from the end edge portion 21Aa toward the main body portion 21D, so that the operating body 21 can be used for the engagement portion C and the lock portion D. Both the reaction force from the lock part D in the state of contacting both and the reaction force from the lock part D in the low-speed transmission state could be received. Further, by providing the contact portion 21E at the end of the main body portion 21D, the deformation portion 21C of the operating body 21 is allowed to be elastically deformed until the contact piece 21A comes into contact with the contact portion 21E. After 21A contacts the contact portion 21E, it does not elastically deform. As a result, excessive deformation of the deformation portion 21C can be easily prevented, and the durability of the operating body 21 can be improved.
- the actuating body 21 elastically deformed when receiving a reaction force from the lock portion D, shifting to the high torque side is preferentially performed at high loads, and reliable output is achieved. Became possible. Since the operating body 21 is provided with the deforming portion 21 ⁇ / b> C that is elastically deformed on both the left and right sides from the rotation center, the above-described effect can be obtained in both the left and right rotation directions.
- the operating body 21 does not necessarily need to be provided separately from the deformable portion 21C and the main body portion 21D, and may be configured integrally. Further, the abutting piece 21A itself may be configured to be elastic so as to be deformable against a reaction force from the lock portion D.
- the load-sensitive transmission of another embodiment (c) includes a shaft-shaped output shaft 2, and a cylindrical input shaft 1 that is rotatably fitted around the lower end portion of the output shaft 2. , A planetary gear transmission mechanism P, and a mission case M at a position covering these.
- a plate 1P is connected to the lower end of the input shaft 1, and a worm gear 1W is provided on the outer periphery of the plate 1P.
- a driving force from an electric motor or the like is transmitted to the worm gear 1W.
- the output shaft 2 when the load acting on the output shaft 2 is less than the set value, the output shaft 2 is driven in a high-speed transmission state in which the speed is equal to the rotational speed of the input shaft 1. Further, when the load acting on the output shaft 2 exceeds the set value, the output shaft 2 is driven in a low-speed transmission state that is lower than the rotational speed of the input shaft 1 due to the deceleration by the planetary gear transmission mechanism P.
- the planetary gear speed change mechanism P includes a sun gear 11 formed integrally with the input shaft 1, a ring gear 12 disposed at a position surrounding the sun gear 11, a plurality of planetary gears 13 engaged with the sun gear 11 and the ring gear 12, and a plurality of planetary gears 13.
- the planetary gear 13 and the carrier 14 capable of revolving are provided.
- the carrier 14 includes a plurality of idle shafts 15 that freely support the three planetary gears 13, and includes a carrier ring 14 ⁇ / b> A that is coupled to the ends of the plurality of idle shafts 15.
- the input shaft 1 and the output shaft 2 are arranged on the same axis as the main axis X, and the axis of the sun gear 11 and the axis of the ring gear 12 (the axis at the center of the ring) on the main axis X and the axis.
- the revolution axis of the carrier 14 is arranged.
- a cam ring 31 that is spline-fitted to the output shaft 2 is provided, and a cam portion 31C formed on the cam ring 31 and a cam portion 14C formed on the carrier 14 are arranged in a positional relationship.
- the output shaft 2 is provided with a bowl-shaped support plate 2P, and a compression type coil spring 17 (an example of an urging member) is provided between the support plate 2P and the cam ring 31, whereby respective cam portions 31C, 14C are provided. The urging force to contact is obtained.
- the cam portion 31C of the cam ring 31 and the cam portion 14C of the carrier 14 displace the cam ring 31 upward even when the output shaft 2 and the input shaft 1 are rotationally displaced relative to each other about the main axis X. It has a shape to be made.
- a shift ring 32 is provided that operates along the main axis X in conjunction with the displacement of the cam ring 31 in the direction of the main axis X.
- a first contact portion 32A that contacts the carrier 14 is formed on the lower surface of the shift ring 32, a second contact portion 32B that contacts the inner surface of the transmission case M is formed on the upper surface, and the ring gear 12 and the outer end position.
- the 3rd contact part 32C which contacts is formed.
- the cam ring 31 when the load acting on the output shaft 2 is less than the set value, the cam ring 31 is in the reference position as shown in FIG. It is in high speed transmission position.
- the first contact portion 32 ⁇ / b> A contacts the upper surface of the carrier 14.
- the cam ring is changed from the change in the relative rotational attitude about the main shaft core X between the carrier 14 and the cam ring 31 as shown in FIG. 31 reaches the shift position, and the shift ring 32 reaches the low-speed transmission position.
- the second contact portion 32B contacts the inner surface of the transmission case M.
- the third contact portion 32C at the outer end thereof is in contact with the ring gear 12, and the first contact portion 32A on the lower surface of the shift ring 32 is the carrier. 14, the entire planetary gear speed change mechanism P is rotated integrally to rotate the input shaft 1 and the output shaft 2 at the same rotational speed, thereby realizing a high-speed transmission state.
- the first contact portion 32A on the lower surface of the shift ring 32 is in contact with the carrier 14 while maintaining the state where the third contact portion 32C at the outer end is in contact with the ring gear 12.
- the second contact portion 32B on the upper surface of the shift ring 32 newly contacts the transmission case M to lock the rotation of the ring gear 12 and realize a low-speed transmission state in which the rotation of the carrier 14 is allowed.
- the cam ring 31, the cam portions 14C and 31C, and the coil spring 17 constitute the load acquisition means A. Further, the shift ring 32, the cam portions 14C and 31C, and the coil spring 17 constitute a switching means B.
- the transmission mode may be set so that the planetary gear transmission mechanism transmits the driving force of the input shaft to the ring gear and decelerates by preventing the rotation of the sun gear.
- the load acquisition unit A may have the same configuration as that of the above-described embodiment.
- Switching means B puts the sun gear in a freely rotating state in a high-speed transmission state, connects the ring gear and the carrier and rotates them together, releases the connection between the ring gear and the carrier in a low-speed transmission state, and prevents the sun gear from rotating. It becomes the composition to do.
- the switching means B sets the sun gear to the free rotation state and connects the ring gear and the carrier to rotate them integrally. Realizes high-speed transmission.
- the switching means B releases the connection between the ring gear and the carrier and prevents the sun gear from rotating, thereby realizing a low-speed transmission state due to the deceleration of the planetary gear transmission mechanism.
- the planetary gear transmission mechanism may be a combination of a plurality of planetary gear transmission systems.
- the rotational speed of the input shaft planetary gear transmission system is transmitted to the sun gear of the next stage planetary gear transmission system to greatly reduce the rotational speed of the input shaft and transmit it to the output shaft.
- the switching means B using the operating body described in the embodiment can be provided in all of the plurality of planetary gear transmission systems, or can be provided in a part of the plurality of planetary gear transmission systems. With this configuration, a high-speed transmission state and a low-speed transmission state are realized.
- the present invention can be applied to all drive systems that actuate an object with a rotational driving force from an actuator.
- it can be optimally used for a load whose load fluctuates during the operation of the object.
Abstract
Description
前記出力系に作用する負荷の大きさを、機械的な作動量として取り出す負荷取得手段を備え、この負荷取得手段で取得した負荷が設定値未満である場合には、前記サンギヤと前記リングギヤと前記プラネタリギヤと前記キャリアとを一体回転させ、前記負荷取得手段で取得した負荷が前記設定値を超える場合には、前記サンギヤと前記リングギヤとのうち駆動力が入力するもの以外の回転を阻止しながらキャリアの回転を許容する切換手段を備えている点にある。
つまり、特許文献1に示されるように、高速伝動状態を実現する伝動系と低速伝動状態を実現する伝動系との2種の伝動系を備え、この2種の伝動系を選択するための2種のクラッチ手段を備えるものと比較すると、本発明の伝動系は簡素化する。また、本発明の構成では、高速伝動状態と低速伝動状態との切換を行う際には、切換手段が遊星ギヤ伝動機構の構成要素の一部の機能を制御するため、高速伝動状態と低速伝動状態との何れの伝動状態においても駆動力は遊星ギヤ伝動系を介して出力系に伝えられることになり伝動系の大型化を抑制する。
特に、遊星ギヤ機構では減速を実現するための2種の伝動形態が考えられる。その1つが、リングギヤを固定する状態において、サンギヤに入力した駆動力をキャリアから出力するものである。他の1つが、サンギヤを固定する状態においてリングギヤに入力した駆動力をキャリアから出力するものである。このような理由から、サンギヤとリングギヤとのうち駆動力が入力するもの以外の回転を阻止することで減速状態を実現する。
その結果、負荷に感応して自動的な変速が行われる変速装置が少ない部品点数で構成できたのである。
前記負荷取得手段が、前記リングギヤの軸芯と同軸芯で相対回転自在に支持される作動リングと、この作動リングと前記リングギヤとの相対回転姿勢を中立姿勢に付勢する付勢部材と、前記キャリアに作用する負荷に連係して姿勢が変化するように前記キャリアと前記リングギヤとに連係する作動体とを備え、この作動体は、前記キャリアと前記リングギヤとの相対回転姿勢が中立姿勢にある際に高速伝動姿勢にあり、相対回転姿勢が前記中立姿勢から外れた際に低速伝動姿勢に達するように構成されてもよい。
複数の前記係合部が、前記キャリアの軸芯を中心にしたギヤ状に形成され、
複数の前記ロック部が、固定系としてのギヤケースの内面に対して前記キャリアの軸芯を中心にした外歯ギヤ状又は内歯ギヤ状に形成されてもよい。
前記負荷取得手段が、前記出力軸に対してトルク伝動自在、かつ、この出力軸の軸芯に沿って移動自在なカムリングと、このカムリングと前記キャリアとの対向する面に形成されたカム部と、前記カムリングを前記キャリアの方向に付勢する付勢部材とを備えて構成されると共に、前記出力軸に作用する負荷が設定値未満である場合に前記カムリングが基準位置にあり、前記出力軸に作用する負荷が前記設定値を超える場合には前記カムリングが前記キャリアから離間するシフト位置に達するように構成され、
前記切換手段が、前記リングギヤとの接触状態を維持しながら、前記カムリングが基準位置にある際に高速伝動位置にあり、前記カムリングがシフト位置にある際に低速伝動位置にあるシフトリングを備えて構成されると共に、このシフトリングは、前記高速伝動位置にある際に前記キャリアに接触することでリングギヤとキャリアとの一体回転させる第1接触部を備え、前記低速伝動位置にある際に固定系に接触することでリングギヤの回転を阻止する第2接触部を備えてもよい。
〔基本構成〕
図1、図3、図4及び図7に示すように、本発明の負荷感応型変速装置は、入力系として入力軸1と、出力系としての出力軸2とをミッションケースMに備え、このミッションケースMの内部に遊星ギヤ変速機構P(遊星ギヤ伝動系の一例)を備えている。この負荷感応型変速装置は、出力軸2に作用する負荷が設定値未満である場合には、図1、図3、図4に示すように入力軸1の回転速度と等しい速度となる高速伝動状態で出力軸2を駆動する。また、出力軸2に作用する負荷が設定値を超えた場合には図2、図5、図6に示すように遊星ギヤ変速機構Pでの減速により入力軸1の回転速度より低速度の低速伝動状態で出力軸2を駆動する。
この負荷感応型変速装置は、負荷取得手段Aと切換手段Bとを備えている。負荷取得手段Aは、出力軸2(出力系)に作用する負荷の大きさを、機械的な作動量として取り出す。切換手段Bは、負荷取得手段Aで取得した負荷が設定値未満である場合には、サンギヤ11とリングギヤ12とプラネタリギヤ13とキャリア14とを一体回転させる高速伝動状態を実現する。また、この切換手段Bは、負荷取得手段Aで取得した負荷が設定値を超える場合には、リングギヤ12の回転を阻止しながらキャリア14の回転を許容する低速伝動状態を実現する。
このような構成のため、出力軸2に作用する負荷が設定値未満である場合には、コイルバネ17の付勢力により作動リング16とリングギヤ12との相対回転姿勢が図4に示す中立姿勢に維持され、これに連係して3つの作動体21が図3に示す高速伝動姿勢に維持される。
このように負荷感応型変速装置は、出力軸2に作用する負荷を負荷取得手段Aで機械的な作動量として取得する。そして、この負荷が設定値未満である場合には、切換手段Bがリングギヤ12とキャリア14とを連結することにより、遊星ギヤ変速機構Pを一体回転させる状態を作り出し高速伝動状態を実現する。また、負荷が設定値を超える場合には、切換手段Bがリングギヤ12の回転を阻止しながらキャリア14の回転を許容することから遊星ギヤ変速機構Pで減速を行わせ低速伝動状態を実現する。
本発明の負荷感応型変速装置は、上記した実施形態以外に以下のように構成しても良い(この別実施形態では前記実施形態と同じ機能を有するものには、前記実施形態と共通の番号、符号を付している)。
こうした構成により、まず、出力軸2に作用する負荷が設定値未満である場合には、コイルバネ17の付勢力により作動リング16とリングギヤ12との相対回転姿勢が中立姿勢に維持され、これに連係して作動体21が図8及び図10Aに示す高速伝動姿勢に維持される。
作動体21は、必ずしも変形部21Cと本体部21Dとを分けて設ける必要はなく、一体的に構成されていてもよい。また、当接片21A自体がロック部Dからの反力に対して変形可能に弾性を有する構成にしてもよい。
図11に示すように、別実施形態(c)の負荷感応型変速装置は、軸状の出力軸2を備え、この出力軸2の下端部に回転自在に外嵌する筒状の入力軸1を備え、遊星ギヤ変速機構Pを備え、これらを覆う位置にミッションケースMを備えている。入力軸1の下端にはプレート1Pが連結し、このプレート1Pの外周部にはウォームギヤ1W備えられ、このウォームギヤ1Wに対して電動モータ等からの駆動力が伝えられる。この負荷感応型変速装置はどのような姿勢でも使用可能であるが、図11に示す上下関係に従って装置の構成を説明する。
本発明は、遊星ギヤ変速機構が、入力軸の駆動力をリングギヤに伝え、サンギヤの回転を阻止することで減速を行うように伝動形態を設定しても良い。負荷取得手段Aは前述した実施形態と同様の構成で良い。切換手段Bは、高速伝動状態でサンギヤを自由回転状態にするとともにリングギヤとキャリアとを連結してこれらを一体回転させ、低速伝動状態でリングギヤとキャリアとの連結を解除し、サンギヤの回転を阻止する構成となる。
本発明は、遊星ギヤ変速機構が複数組の遊星ギヤ変速系を組み合わせたものであっても良い。その一例として、入力側の遊星ギヤ変速系のキャリアの回転力を次段の遊星ギヤ変速系のサンギヤに伝えることで入力軸の回転速度を大きく減速して出力軸に伝える構成のものを想定できる。このように構成したものにおいて実施形態の記載した作動体を用いた切換手段Bを複数の遊星ギヤ変速系の全てに備えることや、複数の遊星ギヤ変速系の一部に備えることが可能であり、このように構成することにより、高速伝動状態と低速伝動状態とが実現する。
Claims (12)
- サンギヤと、このサンギヤを取り囲むリングギヤと、サンギヤ及びリングギヤに咬合するプラネタリギヤと、プラネタリギヤとともに公転運動することが可能なキャリアと、キャリアの公転運動を取り出す出力系とを備えて遊星ギヤ伝動系を構成すると共に、
前記出力系に作用する負荷の大きさを、機械的な作動量として取り出す負荷取得手段を備え、この負荷取得手段で取得した負荷が設定値未満である場合には、前記サンギヤと前記リングギヤと前記プラネタリギヤと前記キャリアとを一体回転させ、前記負荷取得手段で取得した負荷が前記設定値を超える場合には、前記サンギヤと前記リングギヤとのうち駆動力が入力するもの以外の回転を阻止しながらキャリアの回転を許容する切換手段を備えている負荷感応型変速装置。 - 入力系として前記サンギヤに駆動力を伝える入力軸が備えられ、前記出力系として前記キャリアに連結する出力軸が備えられ、
前記負荷取得手段が、前記リングギヤの軸芯と同軸芯で相対回転自在に支持される作動リングと、この作動リングと前記リングギヤとの相対回転姿勢を中立姿勢に付勢する付勢部材と、前記キャリアに作用する負荷に連係して姿勢が変化するように前記キャリアと前記リングギヤとに連係する作動体とを備え、この作動体は、前記キャリアと前記リングギヤとの相対回転姿勢が中立姿勢にある際に高速伝動姿勢にあり、相対回転姿勢が前記中立姿勢から外れた際に低速伝動姿勢に達するように構成される請求項1記載の負荷感応型変速装置。 - 前記切換手段が、前記作動体と、この作動体が前記高速伝動姿勢にある際にこの作動体に係合して前記キャリアと一体化させる係合部と、この作動体が前記低速伝動姿勢にある際にこの作動体に当接して前記リングギヤの回転を阻止するロック部とを備えて構成されている請求項2記載の負荷感応型変速装置。
- 前記作動体が、前記入力軸および前記出力軸と平行姿勢となる枢支軸を中心にして揺動自在に前記リングギヤに支持されると共に、前記係合部に係合する係合片と、前記ロック部に当接する当接片とを備えており、
複数の前記係合部が、前記キャリアの軸芯を中心にしたギヤ状に形成され、
複数の前記ロック部が、固定系としてのギヤケースの内面に対して前記キャリアの軸芯を中心にした外歯ギヤ状又は内歯ギヤ状に形成されている請求項3記載の負荷感応型変速装置。 - 前記作動リングに前記枢支軸が貫通するように前記入力軸を中心とする円弧状の長孔が形成されるとともに、前記作動体に形成された長孔に対して前記入力軸と平行姿勢となる連係軸が貫通しており、前記連係軸が前記作動リングに連結されている請求項4記載の負荷感応型変速装置。
- 前記作動体を、前記当接片が前記ロック部に当接した際に当該ロック部からの反力を受けて前記当接片が前記ギヤ状の部分に乗り上げた状態で弾性変形可能に構成してある請求項4又は5に記載の負荷感応型変速装置。
- 前記作動体が、本体部と、前記本体部及び前記当接片に連接する変形部とを備え、前記当接片が前記ロック部に当接した際に当該ロック部からの反力を受けて前記当接片が前記ギヤ状の部分に乗り上げた状態で前記変形部を弾性変形可能に構成してある請求項4又は5に記載の負荷感応型変速装置。
- 前記作動体は、前記枢支軸近傍から両端に向けて外周側の前記変形部が内周側の前記本体部と一部切り離された形で延設されており、前記変形部の端部に前記当接片が設けられることで前記変形部は前記本体部及び前記当接片に連接する請求項7記載の負荷感応型変速装置。
- 前記当接片は、前記本体部の端部と離間した状態で前記本体部を覆うL字状に形成されており、前記作動体の端部となる端縁部と、前記端縁部から前記本体部に向けて延びる内縁部とを備え、前記本体部の端部には前記端縁部に接当可能な凸状の接当部が形成される請求項8記載の負荷感応型変速装置。
- 入力系として前記サンギヤに駆動力を伝える入力軸が備えられ、前記出力系として前記キャリアが公転する軸芯と同軸芯上に出力軸が備えられ、
前記負荷取得手段が、前記出力軸に対してトルク伝動自在、かつ、この出力軸の軸芯に沿って移動自在なカムリングと、このカムリングと前記キャリアとの対向する面に形成されたカム部と、前記カムリングを前記キャリアの方向に付勢する付勢部材とを備えて構成されると共に、前記出力軸に作用する負荷が設定値未満である場合に前記カムリングが基準位置にあり、前記出力軸に作用する負荷が前記設定値を超える場合には前記カムリングが前記キャリアから離間するシフト位置に達するように構成され、
前記切換手段が、前記リングギヤとの接触状態を維持しながら、前記カムリングが基準位置にある際に高速伝動位置にあり、前記カムリングがシフト位置にある際に低速伝動位置にあるシフトリングを備えて構成されると共に、このシフトリングは、前記高速伝動位置にある際に前記キャリアに接触することでリングギヤとキャリアとの一体回転させる第1接触部を備え、前記低速伝動位置にある際に固定系に接触することでリングギヤの回転を阻止する第2接触部を備えている請求項1記載の負荷感応型変速装置。 - 前記シフトリングが前記高速伝動位置にある場合に、前記シフトリングの外端に備えられた第3接触部が前記リングギヤに接触して一体化し、前記シフトリングの第1接触部が前記キャリアに接触して前記遊星ギヤ伝達系を一体的に回転させ前記入力軸と前記出力軸とを同じ回転速度で回転させ高速伝動状態を実現する請求項10記載の負荷感応型変速装置。
- 前記シフトリングが前記低速伝動位置にある場合には、前記シフトリングの外端に備えられた第3接触部が前記リングギヤに接触する状態を維持しつつ、前記シフトリングの前記第1接触部が前記キャリアから離間し、前記シフトリングの前記第2接触部がミッションケースに新たに接触して前記リングギヤの回転をロックし、前記キャリアの回転が許容される低速伝動状態を実現する請求項10又は11に記載の負荷感応型変速装置。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112011102250T DE112011102250T5 (de) | 2010-07-01 | 2011-06-24 | Lastempfindliches Gangschaltgerät |
US13/701,771 US20130079189A1 (en) | 2010-07-01 | 2011-06-24 | Load-sensitive gear shifting apparatus |
CN2011900005965U CN203285928U (zh) | 2010-07-01 | 2011-06-24 | 负荷感应型变速装置 |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010151186 | 2010-07-01 | ||
JP2010-151186 | 2010-07-01 | ||
JP2010-218913 | 2010-09-29 | ||
JP2010218913A JP5549877B2 (ja) | 2010-07-01 | 2010-09-29 | 負荷感応型変速装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2012002279A1 true WO2012002279A1 (ja) | 2012-01-05 |
Family
ID=45401996
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2011/064561 WO2012002279A1 (ja) | 2010-07-01 | 2011-06-24 | 負荷感応型変速装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US20130079189A1 (ja) |
JP (1) | JP5549877B2 (ja) |
CN (1) | CN203285928U (ja) |
DE (1) | DE112011102250T5 (ja) |
WO (1) | WO2012002279A1 (ja) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2620578B1 (en) | 2010-09-24 | 2015-10-21 | Aisin Seiki Kabushiki Kaisha | Vehicle door driving device |
JP5935513B2 (ja) * | 2012-05-28 | 2016-06-15 | アイシン精機株式会社 | 負荷感応型変速装置 |
JP6344153B2 (ja) * | 2013-09-19 | 2018-06-20 | アイシン精機株式会社 | 負荷感応型減速装置 |
JP6344154B2 (ja) * | 2014-08-29 | 2018-06-20 | アイシン精機株式会社 | 負荷感応型減速装置 |
FR3028507B1 (fr) * | 2014-11-14 | 2020-11-06 | Pontos | Cabestan compact de forte puissance |
JP6248056B2 (ja) * | 2015-02-20 | 2017-12-13 | オリジン電気株式会社 | 回転方向反転装置 |
CN109654173A (zh) * | 2018-12-28 | 2019-04-19 | 中国电子科技集团公司第二十七研究所 | 一种运动支臂力矩平衡装置 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2003507671A (ja) * | 1999-08-18 | 2003-02-25 | アントーノフ オートモーティブ テクノロジーズ ベスローテン フェンノートシャップ | 特に陸上車両用の変速装置 |
JP2008249006A (ja) * | 2007-03-30 | 2008-10-16 | Kito Corp | 負荷感応型自動変速機を内蔵したチェーンブロック |
JP2009287603A (ja) * | 2008-05-27 | 2009-12-10 | National Institute Of Advanced Industrial & Technology | クラッチ装置 |
JP2010116957A (ja) * | 2008-11-12 | 2010-05-27 | Kito Corp | 負荷感応型自動変速装置と負荷感応型自動変速機を内蔵した巻上機 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3718054A (en) * | 1971-10-07 | 1973-02-27 | Gen Motors Corp | Load responsive torque transmission mechanism |
JPH0954002A (ja) * | 1995-08-19 | 1997-02-25 | Aisin Aw Co Ltd | トルク検出装置 |
US5897454A (en) * | 1996-01-31 | 1999-04-27 | Black & Decker Inc. | Automatic variable transmission for power tool |
KR100195515B1 (ko) * | 1996-12-30 | 1999-06-15 | 마재열 | 자전거의 변환 전진구동 주행의 제어장치 |
FR2768210B1 (fr) * | 1997-09-05 | 1999-11-19 | Antonov Automotive Europ | Procede pour ajuster la progressivite d'un changement de rapport, et dispositif de transmission s'y rapportant |
US6066065A (en) * | 1999-05-04 | 2000-05-23 | New Venture Gear, Inc. | Compounder assembly for automatic transmission |
JP4272780B2 (ja) | 1999-11-19 | 2009-06-03 | 株式会社キトー | チェーンブロックにおける自動変速装置 |
CN101332965B (zh) * | 2008-06-18 | 2010-08-04 | 谢玉枝 | 动力绞车双速控制装置 |
-
2010
- 2010-09-29 JP JP2010218913A patent/JP5549877B2/ja not_active Expired - Fee Related
-
2011
- 2011-06-24 WO PCT/JP2011/064561 patent/WO2012002279A1/ja active Application Filing
- 2011-06-24 DE DE112011102250T patent/DE112011102250T5/de not_active Withdrawn
- 2011-06-24 US US13/701,771 patent/US20130079189A1/en not_active Abandoned
- 2011-06-24 CN CN2011900005965U patent/CN203285928U/zh not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2003507671A (ja) * | 1999-08-18 | 2003-02-25 | アントーノフ オートモーティブ テクノロジーズ ベスローテン フェンノートシャップ | 特に陸上車両用の変速装置 |
JP2008249006A (ja) * | 2007-03-30 | 2008-10-16 | Kito Corp | 負荷感応型自動変速機を内蔵したチェーンブロック |
JP2009287603A (ja) * | 2008-05-27 | 2009-12-10 | National Institute Of Advanced Industrial & Technology | クラッチ装置 |
JP2010116957A (ja) * | 2008-11-12 | 2010-05-27 | Kito Corp | 負荷感応型自動変速装置と負荷感応型自動変速機を内蔵した巻上機 |
Also Published As
Publication number | Publication date |
---|---|
DE112011102250T5 (de) | 2013-05-02 |
US20130079189A1 (en) | 2013-03-28 |
CN203285928U (zh) | 2013-11-13 |
JP2012031986A (ja) | 2012-02-16 |
JP5549877B2 (ja) | 2014-07-16 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5549877B2 (ja) | 負荷感応型変速装置 | |
US10539235B2 (en) | Internal electronic park actuator | |
EP2388497A1 (en) | Parking mechanism for transmission | |
US10935132B2 (en) | Gear shifting apparatus for multi-speed transmission for electric vehicles | |
EP2405162B1 (en) | Park lock apparatus for a transmission | |
WO2008099273A1 (en) | Parking mechanism of automatic transmission | |
EP3324081B1 (en) | Actuator for shift by wire automatic transmission | |
JP2008142862A (ja) | スクリュードライバ | |
KR20180056042A (ko) | 차량용 시트의 릴리즈 액추에이터 | |
EP3140568B1 (en) | Anti-backdrive actuator assembly | |
WO2021117867A1 (ja) | 動力伝達経路切換装置および2段変速機 | |
US11542993B2 (en) | Freewheel | |
JP5935513B2 (ja) | 負荷感応型変速装置 | |
JP6163827B2 (ja) | 車両用パーキング装置 | |
JP2014020445A (ja) | 負荷感応型変速装置 | |
JP5254345B2 (ja) | 車輌のレンジ切換え装置 | |
CN113227598B (zh) | 用于机动车的动力传动系的离合器组件的致动器组件 | |
JP2021173324A (ja) | 解除装置 | |
US10697542B2 (en) | Transmission system having manual override mechanism | |
US11187283B2 (en) | Overrunning clutch | |
JP6344154B2 (ja) | 負荷感応型減速装置 | |
JP2002317871A (ja) | 変速機用電動駆動装置 | |
KR101637513B1 (ko) | 듀얼 클러치 변속기의 구동장치 | |
JP2001349425A (ja) | 変速装置 | |
CN111376716A (zh) | 用于车辆的分动器 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 201190000596.5 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 11800744 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 13701771 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 112011102250 Country of ref document: DE Ref document number: 1120111022506 Country of ref document: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 11800744 Country of ref document: EP Kind code of ref document: A1 |